Resilient mountings



Jan. 20, '1959 Filed May 19, 1952 A. BQ cH| 2,869,811

RESILIENT MOUNTINGS 2 Sheets-Sheet 1 INVENTOR ANTONIO BOSCHI,

BY ga g ,6 9

ATTOR EYJ Jan. 20, 1959 A. BOS'CHI 2,869,811

RESILIENT MOUNTINGS Filed May 19, 1952 2 Sheets-Sheet 2 Loud Deformation Load Deformation Load f1 1 INVENTOR m Deformation ANTONIO BOSCHI,

United Sttes atent O r 2,869,811 RESILIENT MOUNTINGS Antonio Boschi, Milan, Italy, assignor to Societa Appli cazioni .Gomma Antivibranti, Milan, Italy Application May 19, 1952, Serial No. 288,731

7 Claims. (Cl. 248-9) This invention pertains to resilient mountings for machines (especially vehicle motors), and more particularly has reference to elastic supports, primarily for the spring suspension of automotive vehicle engines. It provides an elastic support for machine mountings which require a high degree of resiliency under static load, and also which require effective. stifiening in both vertical directions when oscillations of considerable amplitude are encountered.

It is necessary that these requirements be met, in the case of an automobile engine spring support, in order to properly absorb the vibrations caused by the engine and thus minimize their transmission to the vehicle frame, and also to absorb the shocks caused by rough road conditions and thus substantially prevent the transmission of such shocks from the frame to the engine.

It is accordingly an object of this invention to provide a resilient mounting having a high degree of resiliency under static loads, with resulting low frequency of vibration of the supported machine.

Another object is to provide a resilient mounting having special arrangements to minimize both upward and downward shocks which would otherwise be transmitted by a highly resilient mounting from the supporting frame to the supported machine, owing to the inertia of said machine, as for example, when irregular road prominences and depressions are encountered by a moving motor vehicle.

A further object is to provide a resilient mounting having symmetric limit stops as a part of the special arrangements mentioned in the preceding object of my invention.

With these and other objects in view which may be incident to my improvements, my invention consists in the combination and arrangement of elements hereinafter described and illustrated, by way of example, in

the accompanying drawings, in which:

Figure 1 is a diametral section of an assembled resilient support constructed according .tomy invention,

concentric, rigid, annular plate 7, whose inner portion is embedded in said ring. The rubber ring 5 consists of an upper part 5 (above plate 7), and a lower part 5' (below plate 7); of which the former is pre-stressed by compression between the plate 7 and an upper disc 8 abutting engine 1, and the latter is similarly pre-stressed by compression between said plate 7 and a lower disc 9 supported by bolt 3.

The amount of axial precompression of parts and surface which progressively contacts an increasingly larger area of the plate 8 as-the rubber deforms under superimposed load. It will also be noted that the inner portion of the plate 7 terminates in an upwardly and "ice tained by locking the disc 8 to the upper end of sleeve 6, with any convenient locking device, such as a caulked collar 6*, set into a countersunk hole 8 in the center of disc 8, and by similarly locking the disc 9 to the lower end of sleeve 6 by means of a collar 6 set into a countersunk hole 9 in the center of disc 9.

Considering separately the parts 5 and 5 of ring 5, it will be noted that the former has a dome-shaped outer outwardly bent flange 7 which defines a truncated-conical throat surrounding the sleeve 6 and opposing (in an part 5 are gradually converted into an increasing compression stress between the disc 8 and the truncated cone 1 shaped portion 6 of the sleeve 6 on one side, and between disc 8 and the truncated conical flange 7 of the plate 7 on the other side. The stiffening efiect of this conversion of stresses in the rubber element 5, with increasing load, is indicated by the line A in Figure 2, which clearly shows that the deformation of the part 5 increases with increasing load, in approximately linear proportion, until a selected point, such as a is reached; whereupon further increase in load results in a progressively decreasing deformation of the part 5*, as indicated by the upper curved portion of the line A.

Considering now the part 5 as distinct from the part 7 5*, it will be noted that, as the sleeve 6 descends under load by virtue of the deformation of the part 5, the part 5 is progressively relieved of its pre-compression stresses until it assumes its original unstressed shape; whereupon further lowering of the sleeve 6, under increasing load, results in separating the part 5 from all contact with the disc 9. Conversely, when the sleeve 6 rises under decreasing load, the part 5 is stressed in compression, with a progressively decreasing deformation as the load increases, as indicated by the curve B of Figure 3. The part 5* thus functions as a compression-stressed return buffer which minimizes the rebound of the spring support under shocks caused by rough road conditions.

In the no-load condition (as the support, though assembled, is conventionally shown in Fig. 1), the parts 5 and 5 pre-stressed as aforesaid, are in a balanced state, and such an equilibrium condition corresponds to the part 5*, andv the curve BB corresponds to the curve B of Figure 3, for the part 5 except that the slope of the curve BB is the reverse of the curve B,

' since the load in Figure 4 is indicated as acting in downward direction. The horizontal distance Ob, between the point b on the curve BB and the point 0 on the vertical load axis indicates the amount of precompression of the part 5 under no-load condition of the support. The point 0, where the curves A-A and BB intersect, indicates the point at which the deforma tions of the parts 5 and 5 under the same load, are

41.? equal; and it will be noted that the point m, on the composite load/deformation curve MM (for the entire rubber ring is vertically b'elow the point c, so that :the horizontal distance O m indicates the amount of precompression of the entire rubber ring 5, under no-load condition. 7

Under static load only, the support Works in the vicinity of the point d (on the curve MM of Figure 4), and by suitably adjusting the hardness and degree of pro-stressing of the rubber ring 5, the point "41" can be made to coincide with the point of inflexion (reversal) of the substantially straight line central portion (e-f) of the curve M-M, which corresponds to the highest resiliency. With increasing load, the part 5 is first relieved of its pre-stressing' and then wholly separated from contact with the disc 9, while the part 5 becomes wholly stiff (point 1 in Figure 4), thus acting as a proper limit stop. Conversely, under decreasing load (below point d), the buffer part 5 comes gradually into contact with the disc 9 and this results in a stiffening of the support in the opposite direction. Thus, with a support constructed in accordance with my invention, there is obtained a load/deformation curve (MM in Figure 4) which is substantially symmetric about the static load point d, and slopes gradually in opposite directions beyond its central portion ef.

When my improved support is used for mounting stationary machines, the arrangement is essentially the same as shown in Figure 1, assuming that the reference numeral 1 denotes the base of the machine and 2 denotes the supporting foundation into which the anchor bolts 4 are set. While I have described the elastic ring 5 as composed of rubber, it is to be understood that I use the word rubber in its generic sense, so as to include any similar material having substantially the same properties as rubber.

While I have shown and described the preferred embodiment of my invention, I desire it to be understood that I do not limit myself to the precise details of construction and arrangement of elements disclosed by way of illustration, as these may be changed and modified by those skilled in the art without departing from the spirit of my invention, or exceeding the scope of the appended claims.

I claim:

1. A resilient support for machines comprising: a rubberring having a dome-shaped outer surface and supported at a region intermediate its opposite ends by a rigid, concentric, annular plate having an inner portion flared upwardly and outwardly into a frusto-conical shape and embedded in said ring, and a flat outer portion attached to a supporting base; said ring having an annular, peripheral portion extending below said plate; a flat rigid, annular, load-bearing disc, abutting a portion of the supported machine, and a rigid, annular butter disc attached to said load-bearing disc, in fixed spaced relationship therewith, by a rigid, tubular sleeve passing vertically through the central portion of said ring; said ring being interposed between said discs which are secured by a bolt to the supported machine; said ring and load-bearing disc being so constructed and arranged in relationship with each other that their adjacent surfaces define an intervening angular space which is gradually reduced so that said surfaces contact each other over a progressively by said ring is prestressed in axial compression between 7 said discs to a selected degree during the assembly of said parts in said support.

3. A resilient support according to claim 1, wherein said sleeve has an upwardly flared conical portion on its upper end; the maximum diameter of said flared portion of said sleeve being less than the diameter of said flared portion of said plate, so that said ring is gradually compressed between said load-bearing disc and the flared portions of said sleeve and plate, and is thus deformed at a progressively increasing rate up to selected point under static loading, and is further deformed at .a' progressively decreasing rate as the load on said support is increased beyond said selected point.

4. A resilient support according to claim 1, wherein said ring is bonded to the outer surface of said sleeve.

5. A resilient support according to claim 3, wherein the minimum diameter of said flared portion of said sleeve, is less than the minimum diameter of the opening in said frusto-conical portion of said plate, and said diameters are so related that said ring has a substantially free initial movement in shear and bending, whereby the bending-shearing stresses initially imparted to said rubber ring, when a load is applied to said support, are gradually converted into increasing compression stresses, when said load is increased. I

6. A resilient support according to claim 1, wherein the lower portion of said ring below said plate is tapered downwardly toward said buffer disc which reduces the cross-sectional area of said portion and increases its deformability.

7. A resilient support for machines comprising: a rubber ring having a dome-shaped outer surface and supported at a region'interm'ediate its opposite ends by a rigid, concentric, flat, circular plate having a central aperture defined by an inner portion permanently bent upwardly and outwardly and embedded in said ring; and a rigid, load-bearing sleeve attached to the supported machine and to inner surface of said ring, and having an upper portion above said plate, flared upwardly and outwardly in a shape similar to the bent portion of said plate; the maximum diameter of said flared portion of said sleeve being less than the minimum diameter of the central aperture of said plate, so that, upon application of load to said sleeve, said ring is so deformed as to be first stressed in bending-shear stresses, and then in-v creasingly in compression stresses, as said load increases.

References Cited in the file of this patent FOREIGN PATENTS 463,322 

